JPS63227966A - Continuously working hydraulic unit - Google Patents

Abstract

PURPOSE:To permit a delivery of fluid to be obtained accurately corresponding to a rotary angle, when a rotary driving source is connected, while the rotary angle to be obtained accurately corresponding to a flow amount when driving fluid is circulated, by providing a rotary cam mechanism or the like. CONSTITUTION:If a motor 102 is driven, a cam 68 is rotated through each transmitting means 104, 107, 106. And a device, in which as the cam 65 rotates, each cam follower 69, 70 moves following up to each cam surface 68A, 68B, laterally moves each driving shaft 73, 74 through each bracket 71, 72. As the result, each plunger 51, 56 of each unit pump 95 is driven in a predetermined relation along each cam surface 68A, 68B. The device, which repeatedly actuates each unit pump 95 between plural strokes in accordance with rotation of the cam 68, sucks while delivers fluid. While the device, setting each unit pump 95 in a condition that a phase is shifted every 60 deg. from each other, performs the delivery of each unit pump 95 alternately and continuously.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a continuous working fluid device that can be used as a continuous discharge pump or a fluid driven motor.

[Background technology and its problems] Conventionally, in continuously operating fluid devices, for example, continuous discharge pumps, there have been two types of pumps: (1) a moino pump in which a single thread is engaged between two threaded threads, (2) a vane pump or a gear pump, and (2) a two thread pump. A number of products have been developed, including a linked piston pump and a double-linked plunger pump. but,
Although the above-mentioned Moino Bump has linearity between the rotation angle of the screw and the discharge flow rate, the seal is not self-sealing, so leaks occur, making it unsuitable for sending small amounts of fluid. Vane pumps and gear pumps are Pulsation is unavoidable in the discharged fluid, ■Double piston pumps have slight discontinuities when the pistons switch, making it impossible to keep the discharge flow rate constant;
■Two-barrel plunger pumps also have the problem of slight pulsation.

Incidentally, as technology becomes more sophisticated, there is a demand for a discharge pump that can control minute and precise discharge flow rates. Applications include: - Laboratory use for continuous micro-volume high-pressure applications such as Chroma Dog 9F, and - Continuous application of liquids such as chemical liquids and magnetic powder dispersions to products that are continuously produced such as films. Possible purposes include production factories, chemical factories as variable ratio continuous mixing pumps, and various factories for computer management of other liquids.

However, as mentioned above, none of the conventionally existing pumps has been developed that can continuously discharge even the smallest amount of liquid with high precision. A continuous discharge pump that can also discharge fluid is desired.

Therefore, in Japanese Patent Application No. 61-67696, the present applicant has proposed a plurality of unit fluid devices in which a pair of plungers can be driven at a predetermined distance between first and second ports (suction and discharge ports) separated by a predetermined distance. When used in combination, the pair of plungers are interlocked with a rotating cam mechanism, and when a rotational drive source such as a pulse motor is connected to this rotating cam mechanism, the pair of plungers sucks in and discharges fluid, and The amount of fluid discharged is kept constant as a whole by the action of multiple unit fluid devices, so that the rotation angle and the amount of fluid discharge precisely correspond to each other, so that the amount of fluid discharged is continuous and corresponds to the rotation angle of the rotary drive source. On the other hand, when the driving fluid is supplied between the pair of plungers, the rotating cam mechanism is rotationally driven and the rotation angle of the rotating cam mechanism changes to the amount of supplied fluid, as can be inferred from the case of the continuous discharge pump. A continuous working fluid device is proposed which is designed to be a precisely matched fluid motor.

However, although the continuous working fluid device of this previous application is almost satisfactory in terms of characteristics, it is structurally complex, especially around the rotating cam mechanism, and it is difficult to find a simple structure and reliable operation. Something was desired.

[Purpose of the invention]

The object of the present invention is to discharge fluid that precisely corresponds to the rotation angle when a rotational drive source such as a motor is connected, and to discharge fluid that precisely corresponds to the flow rate when a predetermined driving fluid is distributed. The object of the present invention is to provide a continuous working fluid device that can obtain an angle, has a simple structure, and is reliable in operation.

[Means and effects for solving the problems] The present invention has the following features:
The cam followers that come into contact with the cam surface of the rotary cam mechanism are connected endlessly by wires so as to urge each one toward the cam surface.

Specifically, a hollow port block, a first port and a second port that are communicated with each other within the port block and provided at positions separated by a predetermined distance, and a first port and a second port that are provided within the port block and are located on the same axis, respectively. comprising a first plunger and a second plunger which are inserted so as to be slidable in a direction and whose end surfaces face each other, and a rotating cam mechanism that drives the first and second plungers with respect to the port block in a predetermined relationship; This rotary cam mechanism
a cam having a second cam surface; a first cam follower that abuts the first cam surface of the cam and is connected to the first plunger; a second cam follower connected to a second plunger, and the shape of the first and second cam surfaces of the cam is such that opposing end surfaces of the first and second plungers communicate with the first port. an introduction operation for introducing a predetermined fluid between the two plungers by moving the first and second plungers a predetermined amount in a direction separating them from each other;
, the second plunger is moved in the separating direction by the port block until the fluid portion introduced between the first and second plungers is communicated with the second port while maintaining the relative positional relationship between the first and second plungers. After the first and second plungers have been moved toward the second port, the first and second plungers are moved by a predetermined amount in a direction toward each other. A unit fluid device is configured with a shape having a discharge operation for discharging the fluid introduced between the first and second plungers, and a plurality of unit fluid devices are provided, and each of these unit fluid devices The timing of the operation is set so that the total amount of fluid discharged from each unit fluid device by the rotary cam mechanism is always constant, and each cam follower is attached in a direction in which it comes into contact with each cam surface. This is a continuous working fluid device characterized in that a wire is stretched in an endless manner so as to be energized.

〔Example〕

A first embodiment in which the present invention is applied as a continuous discharge pump will be described below with reference to FIGS. 1 to 9.

In the overall configuration diagram of FIG. 1, the device of this embodiment is roughly divided into three mechanisms, one of which is a fluid-related mechanism 10 shown protruding on the right side of the figure;
0 in a predetermined relationship, and a rotary drive mechanism 1 shown from the left end side to the lower center for rotationally driving this rotary cam mechanism 60.
00.

The fluid-related mechanism 10 includes an outer block 11 that is divided into two left and right parts, and as shown in FIG. Equipped with an inner block storage hole 12 on the inner periphery,
Furthermore, there are eight plunger drive shaft insertion holes 13, two at each corner around the storage hole 12, and one between each two shaft insertion holes 13 at each corner. ,
A total of four bolt insertion holes 14 for attaching the outer block are provided. In addition, the outer block 1 divided into two
1 is integrally fixed with two bolts 15 (see Fig. 2), and the four corners of this integrally fixed outer block 11 are connected to the first
．． As shown in FIG. 2, it is fixed to a front plate 62, which is one end plate of a frame 61 of the rotary cam mechanism 60, by a mounting stay 16 and a bolt 17.

Inside the outer block IfO inner block storage hole I2 is a cylindrical inner block 2 made of ceramic (AI!, □03).
1 is housed therein, and these inner and outer blocks 21.11 constitute a port block 2o. Inside the inner block 21, four plunger insertion holes 22 are formed in the axial direction and are hollow, and at positions near both ends of these four plunger insertion holes 22, that is, at a predetermined distance apart in the axial direction. , there is a communication hole 2 that communicates each insertion hole 22 with each other.
3.24 are bored from the circumferential surface of the block 21 halfway inside the block 21 from opposite directions. The openings of these communication holes 23 and 24 on the peripheral surface of the block are respectively a first port 25 and a second port 26, that is, a suction port and a discharge port. Furthermore, notches 27 and 28 are formed around these first and second ports 25 and 26, respectively, and tube set screws 3 are provided in the outer block 11 at positions facing these notches 27 and 2B, respectively.
1.32 is screwed in. These set screws 31.
32 is hollow, and the first and second tubes 33.34 are inserted through the center hole of the set screw 31.32. The tips of these tubes 33 and 34 are folded back, and the folded ends are fitted with set screws 31 and 32.
The tubes 33 and 34 are sandwiched between the outer block 11 and the inner block 21 by being sandwiched between the outer block 11 and the inner block 21.
That is, it is fixed to the port block 20.

Drain recesses 18 are connected to both ends of the inner block storage hole 12 of the outer block 11, and two drain holes 19 are formed in each of the recesses 18 at both ends. 19 is each O-ring 35
The recess 18 is sealed by a seal screw 36, and by loosening the seal screw 36, the fluid accumulated in the recess 18 can be discharged.

The corners of both end faces of the inner block 21 and the outer block 11
An O-ring 37 is interposed between each corner of the inner block storage hole 12 to form a seal. Moreover, between both end surfaces of the inner block 21 and the inner end surface of the drain recess 18 of the outer block 11, a seal unit 1-1 is provided at a position corresponding to each plunger insertion hole 22.
40 is interposed, and each pair of first and second plungers 51 is inserted into each plunger insertion hole 22 of the inner block 21.
．． 56 and the inner end surface of the drain recess 18 of the outer block 11.

As shown in an enlarged view in FIG. 5, the seal unit 70 includes a holder 41 made of a synthetic resin such as polyacecool, and an outer crotch portion formed on the outer periphery of the holder 41 on the outer block abutting side. The outer O-ring 42 engaged with the outer O-ring 41A and the plunger 51 are interposed in the inner step 41B formed on the inner periphery of the inner block abutting side of the holder 41.
．． A slipper seal 43 made of synthetic resin such as polytetrafluoroethylene (trade name: Teflon) is in sliding contact with the outer peripheral surface of the slipper 56, and the slipper seal 43 is interposed between the slipper seal 43 and the inner step 41B of the holder 41. It consists of an internal O-ring 44 that pops up a seal 43.

The first and second plungers 51.56 are ceramic plunger bodies 52.57 inserted into the plunger insertion holes 22 of the inner block 21, as shown in FIG.
and a metal spatula 53.58 fixed to the outer ends of these bodies 52.57, and the connection of these heads 53.58 to the plunger body 52.57 is through a small diameter neck. 53A and 58A.

The rotary cam mechanism 60, as also shown in FIG.
A rear plate 6 is connected to the front plate 62 via a connecting bar 63 (see FIG. 1) and constitutes a frame 61 together with the front plate 62.
4, and a cover 65 is provided between the rear plate 64 and the front plate 62.
covered by.

Further, the rotary cam mechanism 60 includes the front plate 62 and the rear plate 6.
The cam 6 is rotatably supported via two radial bearings 66 and one thrust bearing 67 on the cam 4.
8, and four first and second cam followers 69 and 70 each consisting of a roller are alternately abutted on the pair of cylindrical end face first and second cam surfaces 68A and 68B of this cam. has been done. These cam followers 69,
70 is a side U-shaped bracket 71 and 72, respectively.
Each of these four brackets 71 and 72 is rotatably supported one after the other, making one set, making a total of four sets. Each of these sets has a first and a second cylindrical end surface.
The cam followers 69.70 are arranged on the circumferential surfaces of the cam surfaces 68A, 68B at equal intervals, that is, at 90 degree intervals, and are attached to the brackets 71.72 of each set.
8, each forming an angle of 30 degrees with respect to the central axis of 8, so as not to interfere with each other.

FIG. 7 shows a pair of first and second cam surfaces 6 of the cam 68.
The cam diagrams showing the shapes of 8A and 68B are shown. Both cam surfaces 68A and 68B have the same shape and are point symmetrical.
The shape is rotated by 80 degrees, and the second cam surface 68
B is arranged at a position advanced by 30 degrees in the circumferential direction with respect to the first cam surface 68A, and this advance angle of 30 degrees corresponds to the arrangement angle of the cam followers 69 and 70.

Therefore, the second cam surface 68B shown by the chain line in the figure is shown by moving the second cam surface 68B in a direction that is 30 degrees behind the first cam surface 68A, and by moving it to the height position of the first cam surface 68A so that it overlaps with the second cam surface 68B. It is. These cam surfaces 68B and 6
The substantially parallelogram-shaped portion surrounded by 8A is the difference in movement of the cam followers 69 and 70, and this difference causes the liquid suction and discharge operations, ie, the pumping action, to be described later.

Each of the above 1. The first and second cam followers 69.70 of m are:
Inner block 21 in each of the fluid-related mechanisms 10
It is designed to interlock with a pair of plungers 51 and 56 inserted into each of the four plunger insertion holes 22, respectively. That is, a first plunger drive shaft 73 is attached to the end of one bracket 71 on the front plate 62 side, and a second plunger drive shaft 74 is attached to the same end of the other bracket 72 (on the front plate 62 side). These shafts 73 and 74 are fixed and extend through a total of eight plunger drive shaft insertion holes 13 formed in the outer block 11 of the fluid-related mechanism IO.

A base portion of a clamp 76 whose one end surface is locked by a retaining ring 75 is inserted into the middle of the first shaft 73, and one end of a vibrator 77 fitted onto the shaft 73 is inserted into the other end surface of the clamp 76. The other end of this pipe 77 is slightly protruded from the tip of the shaft 73, and this vibe 77
A washer 78 is brought into contact with the protruding end of the shaft 73 , and a bolt 79 is screwed onto the tip of the shaft 73 through the washer 78 .
6 is pressed against the retaining ring 75. A slotted groove 76A is formed in this clamp 76 except for a portion of the base portion through which the shaft 73 is inserted, and
A substantially U-shaped notch groove 76B is formed on one side divided by this slot groove 76A, and this notch groove 76B is the first one.
It is engaged with the neck portion 53A of the head 53 of the plunger 51. At this time, the groove width of the slotted groove 76A of the clamp 76 is made slightly larger than the thickness of the top of the head 53 of the plunger 51, and when no force is applied to the clamp 76,
The notch groove 76B of the clamp 76 is connected to the neck portion 53A of the head 53.
On the other hand, when the base of the clamp 76 is pressed through the pipe 77 by screwing the bolt 79 into the shaft 73, the clamp 76 engages with the slotted groove 76A.
is deformed so that the head 7 of the plunger 51 becomes narrower.
3 can be fixed without any play. Therefore, when the shaft 73 is moved in the axial direction, the first plunger 51 is moved together in the axial direction via the clamp 76.

The second plunger 5 is connected to the second plunger drive shaft 74 in the same manner as the first plunger drive shaft 73.
6 are connected. At this time, the second plunger 56
Since the first plunger 51 is protruded on the opposite side to the outer block 11, the arrangement of each member for connection attached to the second shaft 74 is different from that of the first shaft 7.
This is different from case 3. That is, the second shaft 7
A retaining ring 80 is attached to the middle of the shaft 74, and a vibrator 81 is fitted onto the shaft 74 so as to be in contact with the retaining ring 80. The length of the vibrator 81 does not reach the tip of the shaft 74, and the base of a clamp 82 having the same structure as the clamp 76 is inserted into the tip of the shaft 74 protruding from the pipe 81. The outer end surface of this clamp 82 is made to protrude slightly from the tip of the shaft 74, and the clamp 82 is fixed to the shaft 74 by a bolt 84 that passes through the clamp 82 and washer 83 and is screwed into the tip of the shaft 74. being done.

This clamp 82 also has a slotted groove 82A and a notched groove 82B.
This notched groove 82B is engaged with and fixed to the neck portion 58A of the head 58 of the second plunger 56, so that the movement of the second shaft 74 can be directly transmitted to the second plunger 56.

A total of eight brackets 71, four each. Of '72,
In this embodiment, except for one of the brackets 71, there are two corners on the same side of the first and second cam surfaces 68A and 68B as the first and second cam followers 69 and 70 are provided. , pulleys 87, 88 are rotatably supported, respectively, and each bracket 71 .
72 cam followers 69 and 70 each have a cam surface 68A
.

1 in a zigzag manner so that it is biased in the direction of contacting 68B.
The wire 89 is turned with sufficient tension. Both ends of this wire 89 are fixed to the only bracket 71 that is not provided with the pulleys 87, 88, so that the wire 89 is looped endlessly between each bracket 71, 72 and connected to each cam follower 69. 70 to cam surface 6
It is designed to be in constant contact with 8A and 68B. At this time, the fixing of both ends of the wire 89 to the bracket 71 is as follows:
As shown in FIG. 1, the positions of the arms 90, which are provided with both ends protruding from both sides of the bracket 71 at the same position where the pulleys 87 and 8B of the other brackets 71 and 72 are provided, are adjusted respectively. This is done by fixing each end of the wire 89 to one end of an adjustment screw 91 that is screwed in, and by rotating these adjustment screws 91, the tension of the wire 89 can be set to an appropriate value. There is. Furthermore, a lock nut 92 is screwed onto the other end of the adjustment screw 91 to lock the adjustment screw 91. At this time, each bracket 71.7
The rotation state of the second pulley 87, 8B is the same as the eighth
It is better to refer to the figure, but in order to avoid confusion in the drawing and make it easier to understand, this figure shows two pulleys 87,
8B is made into one each, and the other bracket 72, which should be located on the opposite side of one bracket 71 with respect to the cam 6B, is placed on the same side as the bracket 71, and the structure of each part is also simply drawn. .

In addition, on the rear plate 64 side of each of the brackets 71 and 72,
Support rods 93 and 94 are connected to each other, and each of these support rods 93 and 94 is slidably supported by the rear plate 64, so that each bracket 71 and 72 is supported at both ends.

Here, each pair of first and second plungers 51
．． 56 is inserted into each part of the outer block 11 and inner block 21, and the seal unit 40 fitted to the part
, and each pair of first and second plungers 51 .
56 via clamps 76 and 82, respectively.
, second plunger drive shafts 73, 74, these shafts 73, 74 are connected to the first and second cam surfaces 68 of the cam 6th.
First and second cam followers 6 driven along A and 68B
9, 70, brackets 71, 72, and other components each constitute a unit pump 95 as a unit fluid device. Therefore, the continuous fluid system of this embodiment is composed of a total of four unit pumps 95.

The rotational drive mechanism 100 includes the front plate 62 and the rear plate 6.
A motor 102 as a rotational drive source is attached to a base plate 101 that supports 4 so that its position can be adjusted. There is.

A timing belt 107 is connected between a timing pulley 104 fixed to the output shaft 103 of the motor 102 and a timing pulley 106 fixed to the protruding end of the cam 68 from the rear plate 64 via a tabular bush 105.
The hook is turned so that the cam 68 is rotated by a predetermined angle as the motor 102 is driven. Further, the rotational drive mechanism 100 connects the motor 102 to the base plate 101.
The adjusting bolt 110 is provided with a slide plate 108 that is attached to the slide plate 108 in a position-adjustable manner, and is screwed into the upper end bent portion 108A of the slide plate 108 in a position-adjustable manner, and has its tip abutted against the stopper 109 of the base plate 101. This slide plate 10 is equipped with a lock nut 111 for locking a bolt 110.
By adjusting the position of B, the timing belt 107 is prevented from loosening. Further, an end cover 11 is provided on the left side of the rear plate 64 so as to cover the timing pulleys 104, 106, etc.
2 is provided.

Note that material number 5 in FIGS. 1 and 2 is a cover that covers the periphery of the fluid-related mechanism 10.

Next, the operation of this embodiment will be explained with reference to FIGS. 8 and 9.

In FIG. 1.6, when the motor 102 is driven, the cam 68 is rotationally driven via the timing pulley 104, timing belt 107, and timing pulley 106. As the cam 68 rotates, the first and second cam followers 69.70 move following the shapes of the first and second cam surfaces 68A and 68B, and the first and second cam followers 69.70 move through the brackets 71.72.
Move the second plunger drive shaft 73, 74 from side to side. By driving the brackets 73 and 72, the first and second plungers 51 and 56 of each unit pump 95 are driven in a predetermined relationship along the shapes of the cam surfaces 68A and 68B.

FIG. 8 shows the first and second cam surfaces 68A on the 6th day of the cam,
68B and the first and second plungers 51 of each unit pump 95
．． 56 is shown. Here, although the drawing in FIG. 8 is simplified as mentioned above, the operation is exactly the same, so the operation will be explained based on this diagram.
In addition, in FIG. 8, (A) to (D) indicate each of the four unit pumps 95, and the operation timing of each unit pump 95 is as shown in FIG. There is. In this figure, the leftmost unit pump 95 (A) is in the closest state with the first and second plungers 51 and 56 facing each other with a slight gap between their end surfaces, and The proximal surface is in communication with the first port 25 . This state is a state immediately before a predetermined liquid (fluid) is to be sucked from a liquid (fluid) tank (not shown) connected to the first port 25.

Therefore, the first port 25 acts as a suction port. In this state (A), the reason why the first and second plungers 51.56 are not brought into direct contact with each other even when they are closest to each other is to prevent the movement of both plungers 51.56 from directly contacting each other. Cam surface 68A of cam 6th,
It is intended to follow the shape of 68B as it is.

If both plungers 51.56 are brought into direct contact, the positions of both plungers 51.56 will be determined by this contact, and the plungers 51.56 will not be able to move in accordance with the shapes of the cam surfaces 68A, 68B. It is.

Next, the unit pump 95 in the state of (B) is provided at a position rotated by 90 degrees from the unit pump 95 in (A), and therefore, the cam 68 is located in the figure with respect to the unit pump 95 in (A). The same state is shown after being rotated by 90 degrees in the direction of the middle arrow. In this unit pump 95 of (B), the first
Since the first cam surface 68A of the plunger 51 is in a flat state, the plunger 51 maintains the same height position as in the state (A) above, while the second plunger 56 has a flat first cam surface 68A.
Since B is a cam surface in the upward direction, the cam surface moves away from the first plunger 51 to form a predetermined gap between the end surfaces of the first and second plungers 51 and 56, and the A predetermined liquid is sucked (introduced) from the first port 25. The function of this state (B) is inhalation (
Introduction) is an operational function. Further, the volume of the gap formed between the first and second plungers 51 and 56 in the step (B) corresponds to the amount of liquid sucked.

Next, when the state (C) is reached, the cam 68 is further moved by 90
After several rotations, the first plunger 51 starts to rise along the first cam surface 68A, which is an upwardly inclined surface, while the second plunger 56 is moved from the upwardly inclined surface to a second horizontal surface. Due to the action of the cam surface 68B, the rise has already been completed and it is in the stopped state, and in this stopped state, the end face of the second plunger 56 is in a state of communicating with the second port 26, so that the rise of the first plunger 51 does not occur. Accordingly, the predetermined liquid that has been sucked into the first and second plungers 51 and 56 is discharged to the outside from the second port 26.

Therefore, the second port 26 acts as a discharge port.

In addition, in the intermediate stage of transition from state (B) to state (C), both cam surfaces 68A and 68B are in a state where they are parallel upwardly inclined surfaces, and during this period, the first and second plungers 51, 56 are moved in parallel while keeping the distance between their end faces constant, and the liquid between the end faces of both plungers 51 and 56 is transferred from the first port 25 to the second port 26 side. This switching from (B) to (C) is defined as a valve switching operation, and the state of (C), that is, the state in which the first plunger 51 approaches the second plunger 56 side, is defined as a discharge operation. Also, these first. Second plunger 5
The locus of movement of the end face portion at an angle of 1°56 is shown as a dashed line in the figure, and this locus of movement coincides with the substantially parallelogram shape explained in FIG. 7 above.

Next, when the state (D) is reached, the first plunger 51 has finished rising, and the first plunger 51 and the second plunger 56
The state in which the end faces are closest to each other is carried out immediately before the state of (D), and furthermore, the first plunger 51 is in a descending process,
However, the second plunger 56, which had been stopped at the upper end, is also shown to have moved to the lowering process. The first and second plungers 51, 56 are lowered in a state where both end surfaces are brought closest to each other. This state (D) is 90% from state (C)
If the state is rotated by 90 degrees from the state (D), the state returns to the state (A).

In order to move from state (D) to state (A), both the first and second plungers 51 and 56 are moved while their end surfaces are kept closest to each other, and from state (D) to state (A). The switching is the valve switching process (return).

As the cam 68 rotates in the direction of the arrow in FIG. 8 in this way, each unit pump 95 repeats the cycle from state (A) to state (D) and back to state (A).
The operation of sucking in a predetermined liquid from a predetermined liquid tank connected to the first port 25 and discharging it from the second port 26 is repeated. Furthermore, during this discharge, the four unit pumps 95 are shifted in phase by 90 degrees, as shown in FIG. 8, and the discharge of each unit pump 95 is performed in succession.

FIG. 9 shows the discharge state corresponding to the rotation angle of the cam 68 of each unit pump 95 explained in FIG. 8. (A) to (D) in this figure are respectively (
It corresponds to unit pumps 95 of A) to (D), and (A)
Focusing on the unit pump 95, the period P from 0 degrees to 90 degrees is the suction process, the period Q from 90 degrees to 180 degrees is the valve switching process, and the period from 180 degrees to 270 degrees is the suction process.
The interval R of 270° to 3° is the discharge process.
The 60 degree section S is the return valve switching process. Also,
The discharge processes of each unit pump 95 are shifted by 90 degrees, and the change in flow rate at the start and end of discharge is opposite to that of the unit pump 95 which is shifted by 90 degrees. Therefore, even when the flow rate changes, the total discharge amount of the adjacent pumps 95 remains constant. Therefore, 4
The total discharge amount of the two unit pumps 95, that is, the total discharge amount, is always kept constant as shown in the lower part of FIG.

Note that in the above description, the operation of rotating the cam 68 in the direction of the arrow in FIG. Since the first and second cam surfaces 68A and 68B on the 6th are formed symmetrically, if the cam 68 is rotated in the opposite direction, the first and second plungers 51 and 56 of each unit pump 95 will move as shown in (D). The state moves from (C) and CB) to state (A), and contrary to the above, the second port 2
It is also possible to suction and discharge fluid by using the 6 side as a suction port and the first port 25 side as a discharge port.

Therefore, the names of the first port, the second port, the suction port, and the discharge port in this embodiment are as described above for convenience of explanation, and the substance thereof changes depending on the mode of use.

In addition, since the inner block 21 and the plungers 51.56, both of which are made of ceramic, are selectively fitted after checking the dimensions, there is a gap between the plunger insertion hole 27 and each plunger 51.56. Fluid leakage can be minimized using current processing technology, but it cannot be completely eliminated, and a small amount of leakage still occurs. This leakage enters the drain recess 18 from between the seal unit 40 and the end face of the inner block 21 and accumulates therein.

At this time, the space between the seal unit 40 and the plunger 51, 56 is sufficiently sealed by the slipper seal 43 and the inner O-ring 44, and the space between the seal unit 40 and the inner end surface of the outer block 11 is sufficiently sealed by the outer O-ring 42. Since the fluid is sufficiently sealed by the seal screw 3, there is no leakage of fluid to the outside.
By loosening 6, it can be discharged to the outside.

According to this embodiment as described above, there are the following effects.

That is, in this embodiment, since suction and discharge are performed using a pair of plungers 51, 56 that move in a predetermined relationship in a linear direction, there is almost no need to worry about fluid leakage at the plungers 51, 56. Therefore, the accuracy of the discharge flow rate can be maintained. At this time, any slight leakage from the peripheral surface of the plunger 51, 56 is allowed to collect in the drain recess 18, so that it may come into contact with the synthetic resin or rubber of the seal unit 40, or remain for a long time after leaking. In the unlikely event that denatured fluid does not return to the first and second ports 25.26 (this can sufficiently prevent impurities from entering the discharged fluid. Also, each plunger 51.5
6 is also driven by the rotary cam mechanism 60 having the cam 68, the mechanism serves as an intermediate wheel and can be manufactured compactly. Furthermore, first and second plungers 51.
The end faces of the plungers 51.56 and cam followers 69.70 are connected without play through clamps 76.82, and each cam follower 69.70 is connected to a single wire 89. Since the cam followers 69.70 are brought into contact with the cam surfaces 68A and 68B, the contact force of each cam follower 69.70 to the cam surfaces 68A and 68B can be equalized, and each cam follower 69.70 is made of precision-machined cam surfaces. Move along the shapes of 68A and 68B (
, one set of cam followers 6 for each rotation of the cam 6
9.70, that is, the plunger 51 of each unit pump 95.
The movements of the pumps 56 are completely equal, and the discharge amount of each unit pump 95 can be made equal. Furthermore, since a plurality of unit pumps 95 are used and each unit pump 95 is linked in a predetermined relationship,
The discharge amount of the fluid-related mechanism 10 as a whole is complemented by the discharge amount of each unit pump 95, and can be kept constant at all times, thereby providing a discharge pump with no pulsation. Furthermore, since the total discharge amount of the fluid-related mechanism 10 is precisely proportional to the rotation of the motor 102, by controlling the rotation angle of the motor 102, a highly accurate flow rate can be maintained regardless of the state and position of the fluid-related mechanism 10. Very small amount, for example 0.0 with one pulse. 1all
It is possible to discharge more than a certain amount of fluid, and it is possible to secure a discharge amount with high linearity with respect to the rotation angle of the rotary cam mechanism 60. Furthermore, the connection between the rotary cam mechanism 60 and the fluid-related mechanism 10 is achieved by engaging the slot grooves 76A, 82A of the clamp 76.82 with the head 53.58, and by engaging the slot grooves 76A, 82A of the clamp 76.82. This is done by simply tightening bolts 79 and 84 using the spring properties of the
, clamp 76 by loosening bolts 79.84.
．． 82 and the head 53.58 of the plunger 51.56 can be easily released, and furthermore, if the outer block 11 is removed from the front plate 62 in this state, the part of the port block 20 that is in contact with liquid can be removed. can be easily removed, and cleaning of the port block 20 can be performed in an extremely short time. Further, since the inner block 21 and the plungers 51 and 56, which are the liquid contact parts, are all made of ceramic, the present invention can be applied to a wide variety of fluids regardless of the quality of the fluid.

In the first embodiment, the inner block 21 is made of ceramic, but the present invention is not limited to this, and as in the second embodiment shown in FIGS. The inner block 121 may be made of synthetic resin such as ethylene chloride (trade name: Daiflon). In other words, in FIG. and,
The seal structure is based on this difference in material, and the other parts are almost the same as in the previous embodiment, so the same reference numerals as in the previous embodiment will be used for the same components, and the explanation will be omitted or simplified.

In FIG. 10.11, the first and second plungers 52.
56 is composed of a ceramic plunger body 52.57 and a metal head 53.58 as in the previous embodiment, while the plunger insertion hole 122 of the inner block 121 is made larger in diameter than in the previous embodiment. Seal units 1.40 are inserted from the end surface side of the inner block 121 into the communication holes 23.24 communicating with the first and second ports 25.26 of these insertion holes 122, respectively.

A spacer 141 made of polyacecool resin or the like is interposed between these seal units 140, and these two seal units 140 and spacer 141 can be removed by a hollow setscrew 142 screwed into the outer block 11. It's stopped. The seal unit 140 is
As shown in an enlarged view in FIG. 12, a seal vibe 144 made of tetrafluoroethylene and a
Two O-rings 1 held at a predetermined distance on the outer periphery of 4
It consists of 45. In addition, the seal vibe 1
44 is formed with a plurality of holes 146 at an intermediate position between the two O-rings 145 to communicate the communication hole 23 or 24 with the inside of the seal vibe 144, and the portion where the O-ring 145 is inserted is thin-walled. The inner surface of the thin part 147 is brought into close contact with the plunger 51 or 56 by the elastic force of the O-ring 145, and a sufficient seal is formed.

The second aspect of the present invention shown in FIGS.
This embodiment also has the advantage of being able to achieve substantially the same effects as the previous embodiment, and being manufactured at low cost. Also,
In this second embodiment, on the outer end side of the seal portion sandwiched between both O-rings 145 in the seal vibe 144, a tongue seal or the like is used as in a general seal structure, and the friction force of the plunger 51.56 is used. may be decreased.

Furthermore, in carrying out the present invention, if the inside of the cover 65 of the rotary cam mechanism 60 shown in FIG. You can improve your sexuality.

Further, in carrying out the present invention, in each of the above embodiments, the fluid involvement mechanism 10 using four unit pumps 95 has been described, but theoretically, two or more unit pumps 95 may be used. However, because the inclination angle of the cam surfaces 68A and 68B of the cam 68 becomes steep, etc., the discharge states of the unit pumps 95 cannot always be smoothly connected, so it is practical to provide about four unit pumps 95. . Further, in each of the above embodiments, an example was explained in which the device of the present invention was simply used as a discharge pump with an accurate discharge flow rate, but as shown in FIG. 13,
A bidirectional actuation cylinder 151 as a drive source of the robot is connected to the fluid-related mechanism 10, and an accumulator 152 is connected in the middle of this connection circuit to respond to changes in the volume of the working fluid due to temperature changes to ensure accurate driving. According to the device shown in FIG. 13, the movement of the cylinder 151 to the right or left can be accurately controlled in extremely small amounts. Further, in each of the above embodiments, the motor 102 is used as a rotational drive source, and the fluid engagement mechanism 10 is driven by the drive of the motor 102 to accurately discharge fluid. As shown in FIG. 14, the fluid-related mechanism 10 may be used as a so-called fluid motor. In other words, in FIG. The first and second plungers 51 and 56 housed in the port block 20 are reciprocated, and this reciprocating drive is transmitted to the rotary cam mechanism 60 to rotationally drive the cam 68, which is driven by a rotary encoder or the like. By transmitting the rotation angle to the driven device 159 via the rotation angle detection mechanism 157 and the brake mechanism 158, the driven device 159 can be rotated accurately by driving the pump 156. In short, the device of the present invention includes a fluid-related mechanism 1O that includes a pair of plungers 51.56 that are housed in the port block 20 and reciprocate, and a rotary cam mechanism 60 that is connected to the plungers 51.56. , the cam follower 69.70 that comes into contact with the cam 68 of this rotating cam mechanism 60 is connected to the cam surface 68A by the wire 89.
, 68B side, and how to use it is to connect a separate motor and use it as a pump device, or connect a separate pump and use it as a fluid motor. .

〔Effect of the invention〕

As described above, the present invention has the advantage that it is possible to provide a continuous working fluid device in which the rotation angle of the rotary cam mechanism and the flow rate of fluid passing through the fluid-related mechanism can be made accurately proportional.

[Brief explanation of drawings]

Fig. 1 is a partially sectional front view showing the overall configuration of the first embodiment of the present invention, Fig. 2 is a side view of Fig. 1, and Fig. 3 is approximately the same as Fig. 4 showing the fluid-related mechanism. 4 is an enlarged sectional view taken along the line IV--IV of FIG. 3, FIG. 5 is an enlarged sectional view of the seal unit used in the above embodiment, and FIG. 7 is a cam diagram used in the embodiment, FIG. 8 is an explanatory diagram of the operation of the embodiment, and FIG. 9 shows the discharge state of the embodiment. An explanatory diagram, FIG. 10 is a sectional view taken approximately along the line X-X in FIG.
Figure 1 is X I -X I! of Figure 10. FIG. 12 is an enlarged sectional view of the seal unit used in the second embodiment, FIG. 13 is an explanatory diagram showing Mr. M using the device of the present invention, and FIG. 14 is a diagram of another example of the device of the present invention. It is an explanatory diagram showing a usage mode. 10...Fluid-related mechanism, 11...Outer block, 20
... Port block, 21 ... Inner block, 25.
...first bow), 26...second port, 40...seal unit, 51...first plunger, 56...
Second plunger, 60... Rotating cam mechanism, 68...
Cam, 68A...first cam surface, 68B...second cam surface, 69...first cam follower, 70...second cam follower, 71°72...bracket, 73...first plunger drive shaft, 74...second plunger drive shaft, 76.82...clamp, 89...
...Wire, 95...Unit pump as unit fluid device, 100...Rotation drive mechanism, 102...Motor as rotation drive source, 121...Inner flock, 140...
...Seal unit, 156...Pump, 157...
・Rotation angle detection mechanism, 158...Brake mechanism, 15
9... Driven equipment.

Claims (3)

[Claims] (1) A hollow port block, a first port and a second port that are communicated with each other in this port block and provided at positions separated by a predetermined distance, and each of which slides in the axial direction on the same axis within the port block. a first plunger and a second plunger which are movably inserted and whose end surfaces face each other, and a rotating cam mechanism that drives the first and second plungers with respect to the port block in a predetermined relationship; The cam mechanism has a first and a second cam mechanism.
a cam having a cam surface; a first cam follower that abuts a first cam surface of the cam and is connected to the first plunger; and a first cam follower that abuts a second cam surface of the cam and the second plunger. a second cam follower connected to the cam, and the shapes of the first and second cam surfaces of the cam are:
A predetermined fluid is introduced between the first and second plungers by moving the first and second plungers by a predetermined amount in a direction away from each other while the opposing end surfaces of the first and second plungers are in communication with the first port. This first and second introduction motion
While maintaining the relative positional relationship between the first and second plungers, the plunger is moved away from the port block until the fluid portion introduced between the first and second plungers is communicated with the second port. 1. After the valve switching operation to move the second plunger and the movement of the first and second plungers toward the second port side, the first and second plungers are moved by a predetermined amount in a direction toward each other, and the first, A unit fluid device is configured with a shape having a discharge operation for discharging the fluid introduced between the second plungers, and a plurality of unit fluid devices are provided, and the timing of operation of these unit fluid devices is is set so that the total amount of fluid discharged from each unit fluid device by the rotating cam mechanism is always constant, and each of the cam followers is biased in a direction in which it comes into contact with each cam surface. A continuous working fluid device characterized in that a wire is stretched in an endless manner. (2) In claim 1, the cam of the rotary cam mechanism is connected to a motor whose drive can be controlled, such as a stepping motor or a servo motor, and the drive of this motor allows continuous operation to discharge a predetermined amount of fluid. A continuous working fluid device, characterized in that it is configured as a discharge pump. (3) In claim 1, the rotary cam mechanism is connected to a rotation angle detection mechanism and a brake mechanism, and is also connected to a driven device, and by supplying fluid to the first port. A continuous working fluid device, characterized in that a driven device is driven according to the amount of fluid supplied.